EP3535481A1 - Kraftwerksanlage mit gasturbinenansaugluftsystem - Google Patents
Kraftwerksanlage mit gasturbinenansaugluftsystemInfo
- Publication number
- EP3535481A1 EP3535481A1 EP17805109.0A EP17805109A EP3535481A1 EP 3535481 A1 EP3535481 A1 EP 3535481A1 EP 17805109 A EP17805109 A EP 17805109A EP 3535481 A1 EP3535481 A1 EP 3535481A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- condensate
- heat exchanger
- load valve
- power plant
- heat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000000034 method Methods 0.000 claims abstract description 13
- 239000012530 fluid Substances 0.000 claims description 23
- 238000011084 recovery Methods 0.000 claims description 18
- 238000010438 heat treatment Methods 0.000 claims description 8
- 239000000203 mixture Substances 0.000 claims description 6
- 238000005457 optimization Methods 0.000 claims description 5
- 230000003068 static effect Effects 0.000 claims description 4
- 239000007789 gas Substances 0.000 abstract description 28
- 239000002918 waste heat Substances 0.000 abstract description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 10
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 8
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- 230000008014 freezing Effects 0.000 description 4
- 238000007710 freezing Methods 0.000 description 4
- 239000000446 fuel Substances 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008092 positive effect Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 1
- 206010053567 Coagulopathies Diseases 0.000 description 1
- 101100033673 Mus musculus Ren1 gene Proteins 0.000 description 1
- 229910002091 carbon monoxide Inorganic materials 0.000 description 1
- 230000035602 clotting Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000002803 fossil fuel Substances 0.000 description 1
- 239000008236 heating water Substances 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000009420 retrofitting Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 239000012086 standard solution Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
- F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/02—Controlling, e.g. stopping or starting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
- F01K17/025—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic in combination with at least one gas turbine, e.g. a combustion gas turbine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/70—Application in combination with
- F05D2220/72—Application in combination with a steam turbine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
- F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/303—Temperature
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
Definitions
- Power plant with gas turbine intake air system The invention relates to a power plant and a Ver ⁇ drive for efficiency optimization and operating range extension .
- Gas and steam turbine plants also referred to as combined cycle power plants, are to be used alongside those that are relevant for continuous operation
- Base load condition also meet other load requirements, alone because of starting and stopping the machines, but especially for changing load requirements in the electrical network.
- the output power of the gas turbine involved can be influenced via the intake mass flow and the turbine inlet temperature.
- a Ver emphasizerervorleit Gla inlet guide vanes
- IOVs inlet guide vanes
- Intake air preheating is also used to prevent icing, to reduce CO emissions at low part load, or at maximum power and low outside air temperatures, resulting in a choked
- Ver Whyrvorleit Research can lead to improve the efficiency ver ⁇ .
- heat exchanger Used in a heat exchanger (heat exchanger) condensed and thus an intermediate circuit typically heated a water / glycol mixture, whereby the cold intake air of the gas turbine was preheated by another heat exchanger. At partial loads, this preheating ensures that the gas turbine can be driven less or not at all throttled and thus a higher degree of efficiency is achieved, resulting in reduced fuel consumption.
- the circuit is simpler here and the efficiency optimization is limited. Limiting effect here is that the heat source low pressure steam should be used both in the steam turbine and in the system of Ansaugluft- preheating.
- Intake air preheating is not enabled for the purpose of improving the partial load efficiency until the block power setpoint has reached a certain value, e.g. 70%, has fallen below.
- the heat exchanger surface could be adjusted.
- the valve position of the water / glycol-side three-way valve, with which the water / glycol mixing temperature is regulated before entry into the air / water heat exchanger was set so that always a fairly large valve opening (eg 60%) is reached.
- hot district heating water or hot condensate from the condensate front-end may be used to prevent ice formation in the gas turbine intake air and to improve carbon monoxide emission.
- these systems are not very flexible and, due to the size of the heat exchanger, utilization of the heat source and the underlying circuit and control limited to a relatively low power and can only very poorly regulate very small benefits.
- the object of the invention is to provide a power plant with ge ⁇ over the prior art improved efficiency and extended operating range.
- Another object of the invention is to provide a corresponding method for efficiency optimization and operating range extension.
- the invention solves the task directed to a power plant by providing that in such a power plant comprising a gas turbine, a waste heat steam ⁇ generator, and an intermediate circuit with a first heat exchanger, which is connected in an air inlet of the gas turbine, and a second Heat exchanger, which is connected in a condensate circuit, the one
- Condensate preheater in the heat recovery steam generator comprises, on both sides of the second heat exchanger, a first or two ⁇ tes high-load valve and parallel to a first or second low-load valve for lower flow rates than by the first and second high-load valve are arranged.
- the condensate circuit comprises a first recirculation line, which has an outlet of the condensate preheater with an input of the
- Condensate preheater connects, with redundant recirculation pumps (i.e., two or more) in the first
- the second heat exchanger with relatively small heat outputs can be operated safely and the risk of evaporation and freezing is further reduced.
- the heat transfer is influenced not only by the inlet temperature but also by the flow and can thus be better adjusted.
- the first branch line branches in the direction of flow to the
- Recirculation pump from the first recirculation line.
- the recirculation pumps can promote the condensate not only by the recirculation directly back to the entrance of the condensate preheater, but also for two ⁇ th heat exchanger, so that no additional pumps are necessary.
- the first high-load valve is arranged in the first branch line and the first low-load valve is arranged around the first high-load valve in a first bypass line.
- the first high-load valve and in a first bypass line to the first high-load valve the first
- a second recirculation line can branch off from the second branch line, which opens into the first recirculation line upstream of the redundant recirculation pumps in the flow direction of a condensate.
- a second recirculation line when the main load and low load valves are arranged together with the first bypass line in the second branch, branch off from the first bypass line, a second recirculation line, which opens in the second case in the flow direction of a condensate before the redundant recirculation in the first recirculation line.
- a third recirculation line branches off from the second branch line and opens into the first branch line.
- a pump in the third recirculation line branches off from the second branch line and opens into the first branch line.
- the condensate has at least two heating surfaces, of which at least one comprises a bypass up, ie in particular the bypass bypasses viewed in the flow ⁇ direction of a condensate last of the heating surfaces and opens into the first recirculation line, for example before the recirculation.
- the second high-load valve in the intermediate circuit and the second low-load valve are arranged around the second high-load valve in a second bypass line, wherein a third Um arrangementstechnisch to the second heat exchanger, followed by a static mixer, is arranged in the intermediate circuit, wherein the second high-load valve fulfills the function of a three-way valve and an output of the second Hochlastven- tils maral ⁇ tet at an input of the second heat exchanger and from a further output of the second high-load valve, the third bypass line branches off.
- Solutions- that the circulating in the intermediate circuit fluid amount is not affected by, son ⁇ countries on the remaining balance can be directed simply at the second heat exchanger past ensures.
- the sometimes large differences in temperature and viscosity of the fluid in the intermediate circuit due to the division of the fluid streams are mixed by the static mixer to a homogeneous level.
- the power plant comprises a device for controlling the first and second high-load and low-load valves.
- the second heat exchanger is at least one fully welded plate heat exchanger.
- the second heat exchanger may well consist of two separate, fully welded plate heat transfer, in particular if one of the two is provided with a bypass, so that the amount of heat transferred to the condensate and thus also the preheating of the intake air can be finer set.
- the object directed to a method for efficiency optimization and expansion of a power plant system is achieved by a method in which a fluid is conducted in an intermediate circuit and thereby heat is transferred via a first heat exchanger to the air sucked by the gas turbine, wherein heat of a preheated condensate is transferred from the heat recovery steam generator via a second heat exchanger to the fluid, wherein the condensate is passed depending on the heat demand via a first high-load valve or a parallel to the first high-load valve, designed for lower flows than the first high-load valve first low-load valve.
- Preheating a stream of preheated condensate is added and the mixture is supplied to the second heat exchanger.
- a AufMapspanne of the intermediate circuit is used as a control variable for a condensate ⁇ mass flow through the second heat exchanger, that is, the temperature- Difference in temperature of the fluid between input and output at the second heat exchanger.
- the condensate mass flow which flows through the condensate-heated second heat exchanger, is thus adjusted according to the heat demand of the intermediate circuit. This ensures that the mass flows of the heated and the heating medium are always in a favorable ratio, which has a positive effect on the operation of the second heat exchanger.
- This mode of operation reduces the risk of Einfrie- proceedings of condensate and also the Ausdampfens the fluid, wel ⁇ ches typically a water is / glycol mixture. This also makes the water / glycol mix temperature control is improved, since now a displacement of the actuator (Dreiwe ⁇ geventil) by a certain amount a constant temperature change causes, that the gain is now constant.
- a valve position of the second high-load valve can be used.
- a temperature setpoint for the intake air is continuously adapted as a function of a proportion of gas turbine at a set nominal power value of the power plant. Since with the invention, the temperature of the intake air is now finely adjustable, it is advisable to continuously adjust the intake air to a calculated based on the akturellen operating state of the power plant optimum.
- a low pressure stage can be accumulated in the heat recovery steam generator, ie, the pressure in the low pressure drum is raised to heat in the heat recovery steam generator
- a high-pressure preheater bypass in the heat recovery steam generator can be opened step-by-step as needed, if necessary in addition to the pressure build-up in the low-pressure range, in order to move heat to the condensate preheater.
- Ansaugluftvormaschinermung be combined with the partial shutdown of burners of the gas turbine, so that it is possible to operate the power plant with good efficiency and ver ⁇ comparatively very low power, the exhaust emissions remain within the permitted range.
- the invention extends the operating range for partial load efficiency improvement. Instead of a constant temperature target value for the intake air at sub ⁇ exceed a fixed limit of the power set ⁇ value pretending the Ansaug Kunststofftemperatursollwert is from ⁇ pending adjusted by the adjusted power target value, so that even at higher partial loads an efficiency improvement is achieved, and the IGV of the gas turbine not open wide or the set power setpoint can be adjusted.
- the advantage of the invention is also in a further increased saving of fossil fuels (gas, oil) in partial loads of a gas and steam power plant and associated clotting ⁇ lower operating costs and emissions and the realization of a large, flexible application.
- Heat source can now be exploited part of the heat energy of the exhaust gas from the last heat exchanger surface of the heat recovery steam generator still partial load operation of the gas turbine combined cycle power plant to increase efficiency and to prevent ice formation in winter operation.
- simultaneous preheating of the gas turbine intake air with hot condensate as the heat source of higher steam from the low pressure drum can be further ge in the steam turbine ⁇ uses.
- the Ansaug Kunststofftemperatursollwert on hand of the current power setpoint can be set so that the maximum temperature allowed for achieving this power is not exceeded during ramping to full load.
- the above-mentioned concept can alternatively also be based on the use of district heating or another hot water heat source or can also be implemented in the combination of both heat sources.
- FIG 1 shows a power plant according to the invention
- Figure 2 shows a power plant according to the invention with different ⁇ alternatives.
- FIG. 1 shows schematically and exemplarily a force ⁇ plant 1 with a gas turbine 2, as well as greatly simplified for the invention-relevant components of a waste heat steam generator 3.
- the preheating of the intake air of the gas turbine 2 is effected via an intermediate circuit 4 for a fluid which is suitable as a heat transfer medium , For example, a water / glycol mixture, with a first heat exchanger 5, which is connected in an air inlet 6 of the gas turbine 2, and with a second heat exchanger 7, which is designed as a fully welded plate heat exchanger and is connected in a condensate circuit 8.
- a fluid which is suitable as a heat transfer medium
- a fluid which is suitable as a heat transfer medium
- a fluid for example, a water / glycol mixture
- a first heat exchanger 5 which is connected in an air inlet 6 of the gas turbine 2
- a second heat exchanger 7 which is designed as a fully welded plate heat exchanger and is connected in a condensate circuit 8.
- a first 10 and second high-load valve 11 and parallel thereto a first 12 and second light load valve first 13 for lower flow rates than by 10 and second high-load valve 11 is arranged.
- the condensate circuit 8 comprises a condensate preheater 9 in the heat recovery steam generator 3, and a first recirculation line 14 which connects an output 15 of the condensate preheater 9 with an input 16 of the condensate preheater 9, where ⁇ redundant recirculation pumps 17 in the first
- the second heat exchanger 7 is integrated into the condensate circuit 8 by a first branch line 18 branches off in the flow direction after the recirculation 17 from the first recirculation line 14 and opens into the second heat exchanger 7 and a second branch line 19 the second heat exchanger 7 with the Input 16 of the condensate preheater 9 connects.
- Um Solutionstechnisch 20 about the first high-load valve 10 angeord ⁇ designated first low-load valve 12 may be arranged either together in the first 18 ( Figure 2) or in the second branch line 19 ( Figure 1).
- the second recirculation line 21 branches off directly from the second branch line 19 and likewise flows in the flow direction of a condensate before the redundant recirculation pumps 17 into the first recirculation line 14 Difference to the first embodiment is therefore only in the branch of the first
- Figure 2 shows an embodiment in which the cooled condensate is not in front of the redundant
- Recirculation pump 17 is fed back, but at the second branch line 19, a third Rezirkulations ⁇ line 22 opens directly into the first branch line 18. In this case, however, a pump 33 is in the third
- the second high ⁇ load valve 11 and in a second Um arrangements effet 23 around the second high-load valve 11, the second low-load valve 13 are arranged in the intermediate circuit 4. Furthermore, a third bypass line 24 is arranged around the second heat exchanger 7, followed by a static mixer 25, in the intermediate circuit 4.
- the second high-load valve 11 is executed in the figure 1 as a three-way valve and an output 26 of the second high-load valve 11 is switched to an input 27 of the second heat exchanger 7 ge ⁇ and from another output 28 of the second high-load valve 11 branches the third Redirection line 24 from.
- Figure 1 also shows a device 29 for controlling the first and second-load 10, 11 and low-load valves 12, 13.
- the control is carried out, among other things Basics ⁇ ge of measured temperatures at different locations or flow rates.
- the power plant 1 comprises for this purpose a temperature measuring point 34 for the preheated intake air and temperature measuring points 35, 36 and 37 for the fluid in the intermediate circuit.
- the temperature measuring point 35 is arranged in the FIGSu ren 1 and 2 between the recirculation pump 43 in the intermediate circuit 4 and a branch to the second bypass line 23, but it can also already before the
- Recirculation pump 43 may be arranged in the intermediate circuit and supplies the temperature of the fluid before the second heat transfer ⁇ 7.
- the temperature measuring point 36 is located immediately behind the second heat exchanger 7 and supplies the temperature of the fluid after the heat exchange with the condensate. The difference between the measured values of the temperature measuring points 35 and 36 is called the heating-up period.
- the mixing is with the temperature measuring point 37 temperature of the fluid is determined, ie the temperature resulting from mixing of the fluid flows through the second heat exchanger 7 or past it and with the first heat ⁇ exchanger 5 is beauf ⁇ beat to warm up the gas turbine intake ,
- Flow measuring points 38, 39 for the condensate are arranged in the figures in the second branch line 19 and in the first recirculation line 14.
- the representation of the control in the figures is greatly simplified. The actual control is more complex and includes of course many other aspects as well as a regulation of the recirculation pumps 17 in the first recirculation line 14. The control does not have to be central for all components as shown in the figures.
- Heat recovery steam generator 3 are opened to move even more heat to the condensate preheater 9. This works both for high-pressure areas with high-pressure drum 40, as shown in FIG. 1, and in the Benson variant shown in FIG.
- Condensate preheater 9 with divided heating surfaces 41, one of which has a bypass 42, so that the amount of heat transferred to the condensate is better adjustable.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Control Of Turbines (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016225983 | 2016-12-22 | ||
PCT/EP2017/078407 WO2018114113A1 (de) | 2016-12-22 | 2017-11-07 | Kraftwerksanlage mit gasturbinenansaugluftsystem |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3535481A1 true EP3535481A1 (de) | 2019-09-11 |
EP3535481B1 EP3535481B1 (de) | 2020-07-08 |
Family
ID=60484326
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17805109.0A Active EP3535481B1 (de) | 2016-12-22 | 2017-11-07 | Kraftwerksanlage mit gasturbinenansaugluftsystem |
Country Status (8)
Country | Link |
---|---|
US (1) | US11162390B2 (de) |
EP (1) | EP3535481B1 (de) |
JP (1) | JP6771665B2 (de) |
KR (1) | KR102242144B1 (de) |
CN (1) | CN110100078B (de) |
ES (1) | ES2823056T3 (de) |
MX (1) | MX2019007623A (de) |
WO (1) | WO2018114113A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018219374A1 (de) * | 2018-11-13 | 2020-05-14 | Siemens Aktiengesellschaft | Dampfturbine und Verfahren zum Betreiben derselben |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1576872B2 (de) | 1967-08-17 | 1970-12-23 | Siemens AG, 1000 Berlin u. 8OOO München | Einrichtung für die Speisewasserregelung von Zwangdurchlaufkesseln im unteren Teillastbereich |
DE59205446D1 (de) * | 1991-07-17 | 1996-04-04 | Siemens Ag | Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage und Anlage zur Durchführung des Verfahrens |
EP0582898A1 (de) | 1992-08-10 | 1994-02-16 | Siemens Aktiengesellschaft | Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage sowie danach arbeitende Gud-Anlage |
DE19512466C1 (de) | 1995-04-03 | 1996-08-22 | Siemens Ag | Verfahren zum Betreiben eines Abhitzedampferzeugers sowie danach arbeitender Abhitzedampferzeuger |
DE19745272C2 (de) | 1997-10-15 | 1999-08-12 | Siemens Ag | Gas- und Dampfturbinenanlage und Verfahren zum Betreiben einer derartigen Anlage |
US6052996A (en) * | 1998-02-13 | 2000-04-25 | Clark; John C. | Heat-work cycle for steam cycle electric power generation plants |
DE19924593A1 (de) | 1999-05-28 | 2000-11-30 | Abb Patent Gmbh | Verfahren zum Betrieb eines Dampfkraftwerkes |
EP1884640A1 (de) | 2006-08-04 | 2008-02-06 | Siemens Aktiengesellschaft | Verfahren zum Betrieb einer Gasturbinenanlage, Steuereinheit sowie Gas- und Dampfturbinenanlage |
EP2256316A1 (de) | 2009-05-28 | 2010-12-01 | Siemens Aktiengesellschaft | Ansauglufttemperiereinrichtung sowie ein Verfahren zum Betrieb einer Ansauglufttemperiereinrichtung |
US8096128B2 (en) | 2009-09-17 | 2012-01-17 | Echogen Power Systems | Heat engine and heat to electricity systems and methods |
BR112013000862B1 (pt) | 2010-07-14 | 2021-07-13 | Mack Trucks, Inc. | Sistema de recuperação de calor desperdiçado com recuperação parcial |
EP2589760B1 (de) * | 2011-11-03 | 2020-07-29 | General Electric Technology GmbH | Dampfkraftwerk mit Hochtemperatur-Wärmespeicher |
DE102012021357A1 (de) * | 2012-11-02 | 2014-05-08 | Diplomat Ges. zur Restrukturierung und Wirtschaftsförderung mbH | Niedertemperatur-Arbeitsprozess mit verbesserter Effizienz für die Elektroenergieerzeugung im Kreisprozess |
KR101996281B1 (ko) * | 2012-12-31 | 2019-07-04 | 대우조선해양 주식회사 | 가스복합발전플랜트의 출력 증대 시스템 |
JP6116306B2 (ja) * | 2013-03-25 | 2017-04-19 | 三菱日立パワーシステムズ株式会社 | ガスタービン用燃料の予熱装置、これを備えているガスタービンプラント、及びガスタービン用燃料の予熱方法 |
EP2808501A1 (de) | 2013-05-27 | 2014-12-03 | Siemens Aktiengesellschaft | Verfahren zum Betreiben einer GuD-Kraftwerksanlage |
DE102013219166A1 (de) | 2013-09-24 | 2015-03-26 | Siemens Aktiengesellschaft | Ansaugluftvorwärmsystem |
EP2868874A1 (de) | 2013-11-05 | 2015-05-06 | Siemens Aktiengesellschaft | Dampfkraftwerk mit einem flüssigkeitsgekühlten Generator |
-
2017
- 2017-11-07 JP JP2019516652A patent/JP6771665B2/ja active Active
- 2017-11-07 KR KR1020197020860A patent/KR102242144B1/ko active IP Right Grant
- 2017-11-07 ES ES17805109T patent/ES2823056T3/es active Active
- 2017-11-07 MX MX2019007623A patent/MX2019007623A/es unknown
- 2017-11-07 US US16/310,558 patent/US11162390B2/en active Active
- 2017-11-07 EP EP17805109.0A patent/EP3535481B1/de active Active
- 2017-11-07 CN CN201780080284.1A patent/CN110100078B/zh not_active Expired - Fee Related
- 2017-11-07 WO PCT/EP2017/078407 patent/WO2018114113A1/de unknown
Also Published As
Publication number | Publication date |
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KR102242144B1 (ko) | 2021-04-20 |
ES2823056T3 (es) | 2021-05-05 |
EP3535481B1 (de) | 2020-07-08 |
WO2018114113A1 (de) | 2018-06-28 |
CN110100078B (zh) | 2021-09-07 |
JP2019530824A (ja) | 2019-10-24 |
US20200318497A1 (en) | 2020-10-08 |
MX2019007623A (es) | 2019-09-05 |
CN110100078A (zh) | 2019-08-06 |
KR20190094438A (ko) | 2019-08-13 |
JP6771665B2 (ja) | 2020-10-21 |
US11162390B2 (en) | 2021-11-02 |
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